ES2656690T3 - Clamping system with anti-false thread - Google Patents

Abstract

An anti-false thread fastening system characterized in that it comprises: a female fastening member comprising: at least one female fastening thread formed in an interior of the female fastening member; at least one female lead thread formed inside the female clamping member; a male clamping member comprising: a stem having a leading end for insertion into the female clamping member; at least one male clamp thread formed on the outside of the stem as a plurality of threads adapted to engage the female clamp thread; at least one male lead thread formed on the outside of the shank at the lead end that is at least half a thread around the shank and comprises a curved profile defined by an arc having a radius approximately equal to a radius of an arc that it is tangent to both flanks of a thread profile of the at least one male clamping thread and below the pitch line of the at least one male clamping thread.

Description

DESCRIPTION

Fixing system with anti-false thread

The present disclosure relates generally to the field of threaded fasteners such as screws and bolts and, more particularly, anti-false thread fasteners.

Threaded fastener technology is basic to the construction or fabrication of most articles of manufacture, such as machines, automobiles, trains, airplanes, engines, and the like. Threaded fasteners can be substantially round bolts, screws, nails, rods, or other members having uniform, non-uniform, or tapered external helical threads that bolt-engage to mating threaded fasteners, such as nuts or holes having helical threads. substantially coincident internal. For proper engagement of the externally and internally threaded fasteners, the longitudinal axis of the externally threaded member must typically be substantially collinear with the longitudinal axis of the internally threaded member. Furthermore, proper engagement of the externally and internally threaded fasteners typically requires that the peak of the external thread of the male helix be aligned with the root of the internal thread of the mating female helix. While this disclosure refers to any thread shape, the International Organization for Standardization (ISO) metric thread will be illustrated as an example of a standard thread, as shown in Figure 1. As used in this application , the designation "thread" can be applied to the entire thread helix of the fastener, or to any partial section of the helix, in which a thread may comprise a partial winding or several windings around the axis of a fastener, in the case of a male clamp member, or a partial wrap or multiple wraps around an inner hole, in the case of a female clamp member.

The inability to achieve proper thread engagement between externally and internally threaded fasteners during assembly is typically due to one of two threading conditions that occur when opposing helixes engage and parts rotate relative to each other. The first, commonly referred to as "cross threading", occurs when there is both angular and linear axial misalignment between the external thread member, typically a bolt or screw, and the internally threaded member, typically a nut or threaded hole. Specifically, the transverse threading is the result of the two members attempting to engage at least half a pitch out of linear alignment, while the respective helical helixes are also angularly misaligned.

Figure 2 illustrates cross threaded male and female clamp members. When the clamping members have cross threads, the male clamping member 10 is not collinear with the female clamping member 30, and the threads wedge when the threaded helixes are rotated against each other. If rotation continues when the threads are in such a wedged condition, then the threads of one or both members will typically be structurally damaged. From AU 2003204363 A1 a fastener with alignment lead thread is known.

The second threading condition that causes proper thread engagement is not achieved is usually called "false threading" which occurs when the two helixes are misaligned in the middle of the pitch, so that the threads engage vertex to vertex at place vertex to root.

Figures 3A and 3B illustrate a false threading condition, in which the helix axes are not misaligned, but are essentially collinear. Internal threads are often manufactured with a slight depression, groove, or crack 32 at the apex of the internal threads. False threading occurs when the apex of an external lead thread 17 engages the groove 32 at the apex of the internal threads, so that the two helixes are mid-pitch misaligned. Figure 3B is a close-up view of the false-threading condition of Figure 3A and illustrates how such grooves 32 at the vertices of the internal threads, while generally small in the main body of the internally threaded helix, can be somewhat deeper and wider at the input end of the propeller - the lead thread section of the internal thread. In such a case, it is possible that the leading thread peak 17 of the externally threaded helix (and / or the first complete helix thread) may try to enter the normal helical root on the opposite internal helix, but instead engage the internally threaded helix in groove 32 at its apex.

Several characteristics of today's widely manufactured internal propeller drive threads greatly increase the likelihood of false thread failures.

First, Figures 4A-4F illustrate how typical mating threads 31 of a female clamping member 30 tend to have a depression, groove, or crack 32 at their vertices, which tend to cause false thread failures. These grooves 32 can be both deep and wide at the inlet end of the propeller. As the groove 32 advances from its start toward the inner helix, it tends to narrow and shallow and, in most fasteners, largely disappears in about a half revolution of the inner helix. As such, the surface that forms the deepest point in the groove 32 tends to grow away from the axis of the internally threaded helix at a rapid rate as the groove 32 in the internal lead thread 31 closes and approaches. the complete thread.

Second, Figures 5A-5B illustrate two side views of a male clamp member 10 having clamp threads 15, in which lead thread 17 may have a profile that is normally pointed and / or has some type of protruding feature in its beak, which tends to cause false thread failures. Figure 6 shows a Side view of a male clamping member 10 having clamping threads 15 and an anti-cross thread 16, wherein the lead thread 17 has a typical profile with a pointed beak. Figure 7 shows a side view of a male clamping member 10 having clamping threads 15, an anti-cross thread 16, and a dog point 22, in which the lead thread 17 has a typical profile that includes a combination curved and flat surfaces with a pointed beak. When the pointed peaks of the lead threads of the male clamping members engage the grooves at the apexes of the internal threads illustrated in Figures 4A-4F, false thread failures can occur.

Third, the relative helix angles of the peaks at the apexes of the internal and external drive threads can cause false thread failures. Internal and external drive threads tend to have different helix angles due to their respective manufacturing procedures. If the helix angle of the external thread peak of the lead thread is greater than the helix angle of the inner peak of the lead thread, then the outer peak bends more severely. This means that, during initial assembly, when the two lead threads make contact, their peaks are not essentially parallel. The most severely bent thread, that is, the one with the largest helix angle, will tend to approach or intersect the other thread at one point on the thread. At the point of intersection of the thread, the pointed tip of the external lead thread may enter the groove at the apex of the internal thread and cause a false thread condition. Other orientation circumstances where the axes of the two threads are not collinear can also lead to false thread failures.

When these features exist individually or in combination to allow the pointed nose of the external lead thread to inadvertently enter the groove in the vertex of the internal lead thread, that external beak may act as if it had been threaded into a normal internal thread. . Since there is no path out of the groove, the point of the external lead thread can continue to follow the groove as the clamping members rotate relative to each other. The slot, however, very quickly becomes narrower and closed, as shown in Figures 4A-4F, such that there is no path for the externally threaded pointed nose to continue threading. The helix angle of the line formed at the bottom of the groove in the internal lead thread is typically somewhat greater than the helix angle of the line formed at the pointed peak of the apex of the external thread. Because these lines are not parallel, that is, the helix angles are different, the threads quickly intersect and the pointed peak of the external lead thread quickly contacts a surface in the groove at the apex of the thread. internal. In this way, the pointed lead thread of the external clamp member can only be freely threaded for a few degrees of rotation until it grows too large for the contraction groove at the apex of the internal thread, not giving it a route to continue threading. Such engagement often results in the pointed nose of the external thread catching or jamming in the groove of the apex of the internal thread. Continuous relative rotation of the clamping members beyond such a false thread jam point often damages or cuts a part of either thread, leading to structural failure of both thread helixes.

Furthermore, many external lead threads manufactured today are shaped such that they have a bulge or rise in height, particularly where the lead thread is very short. If the lead thread is less than half a pitch in length (less than 180 ° around the axis), it can increase in height quickly and thus be more susceptible to false threads. When an external lead thread that has a bulge or sudden rise in height is threaded into a groove at the apex of an internal thread, false thread failures can occur, as described above.

Various types of drive threads are currently used in the industry. In all threaded fastener techniques except tapping screws, the lead thread is used to feed or "drive" the externally threaded helix into the space between adjacent windings of the internally threaded helix. In practice, various forms of lead thread have been used for this purpose. The much more common of these, used in most standard threaded fasteners, is a lead thread device that has historically used part of the first propeller turn to grow from zero height to full thread height and simultaneously to grow wider. During typical manufacturing procedures, this lead thread is allowed to take any free shape that allows it to be easily manufactured. This shape generally includes a 60 degree flank on the side of the helix closest to the clamp head and a free-form flank on the side farthest from the clamp head. The lead thread profile varies significantly with the manufacturing process and from clamping design to clamping design. Due to inherent variations in the manufacturing procedures used to wind this lead thread section, the shape of this section is often inconsistent in shape and unpredictable in growth rate. The variation is most notable in the shape and linear growth in the apex formed at the peak of the external lead thread. (See Figures 5A and 5B). Lead threads typically have a relatively sharp point at the apex of the lead thread because only one flank has a flat surface at the standard 60 ° angle, while the opposite flank surface is freeform at an angle much greater than 60 °, and the two flanks connect directly to each other, rather than through a flat surface parallel to the longitudinal axis of the clamping axis like the other standard threads.

A "non-standard" fastener includes an anti-cross thread described more fully in US Patent 5,730,566. These non-standard fasteners include three threads: the lead thread 17, the anti-cross thread 16, and the clamp threads 15. (See Figure 6). Typical tap threads on fasteners that have anti-cross threads are somewhat different than tap threads on standard fasteners, but are equally susceptible to profile and length variations. The profile of a typical lead thread of a fastener that has an anti-cross thread It has three common characteristics in each section of the lead screw propeller.

First, as shown in Figure 7, the leading thread flank 17b closest to the anti-cross thread 16 tends to maintain a curve similar to half (or less) of that seen in the thread. anti-cross thread 16, in essence, reflecting half of the anti-cross thread 16. The base of this curved lead thread flank 17b shares its root with the anti-cross thread 16. As such, its root appears to be a continuation from the root of the anti-cross thread, and the middle of the lead thread profile appears to be an anti-cross thread profile. As this flank approaches the end of the helix, the curved surface becomes narrower and narrower, finally disappearing at the end of the helix when the lead thread reaches zero height. The other flank of the lead thread 17a tends to be essentially flat and at an angle to the axis of the clamp, at an angle and flatness, as well as convexity and concavity that normally vary significantly and freely in each section, depending on the location on the propeller and manufacturing technique. Typically, the angle, convexity, or concavity of this flank is not controlled during manufacture and varies significantly in angle, growth rate, and contour along the length of the lead thread. As the lead thread traverses around the body, this "flat" flank 17a tends to taper and shrink in height. This "taper" is the result of the root of the flat angled flank getting closer and closer to the root between lead thread 17 and anti-cross thread 16, as lead thread 17 traverses around the axis. . Ultimately, this flat angled flank 17a tapers to zero as the height and width of lead thread 17 decrease towards the end of the helix. Therefore, as this pointed lead thread peak is typically formed of unrestricted free flowing metal, it tends to vary significantly in shape across the length of the lead thread, as well as from clamping to clamping.

Third, the flanks of lead thread 17 tend to form a point rather than a flat or curved vertex at the intersection of the two flanks.

Figures 8A-8C illustrate cross-sectional side views of a typical process for fabricating a fastener from a non-threaded fastener blank by winding between opposing thread rolling dies. In FIG. 8A, the thread rolling dies 40 are spaced to demonstrate the placement of the clamp blank 41 prior to winding. The shaft 12 of the clamping blank 41 normally has a constant diameter to allow the formation of standard threads, and the leading end 14 of the non-threaded clamping blank normally has a chamfer 9 to allow the formation of a thread. Of attack. Figure 8B shows the thread rolling dies 40 in a rolled position such that the threads are being formed in the clamp blank to form the male clamp member 10. In typical manufacturing practices, both fasteners are used. For both standard and anti-cross threads, the threads can be formed by rolling an essentially cylindrical non-threaded clamping blank 41 through thread rolling dies 40. The dies 40 impart the thread profiles onto the unthreaded blank 41 moving the metal into the grooves formed in the thread rolling dies. As shown in Figure 8C, a clamping thread 15 can be formed on the constant diameter shaft portion of the threadless clamping blank by allowing metal to flow through the grooves of the dies until the grooves are fully filled with metal from the blank. The clamp threads 15 formed on the shaft of the clamp tend to have completely uniform profiles because the metal completely fills the grooves in the dies. The lead thread 17, however, can be formed by incompletely filling the grooves of the rolling dies 40 with metal from the chamfered end of the clamping blank. In the lead thread section of the clamp, the thread helix is formed by only partially filling the grooves of the rolling dies. Partial fill occurs because the clamp blank has a chamfer at its end, as shown in Figure 8A.

Figure 8C illustrates a close-up view of the lead thread section shown in Figure 8B. Because the threadless clamp blank has a chamfer at its end, there is not enough metal present in the lead thread area to completely fill the grooves in the thread rolling dies 40. The lead thread 17 For both standard fasteners and anti-cross thread fasteners it is formed by partially filling the die slots in the threaded lead section. Partial fill allows metal to flow freely in a variety of lead thread profiles as described above. Thus, lead thread profiles are inherently inconsistent due to blank, die, and process variation. In more known lead threads, variation is inherent because thread rolling dies allow unrestricted free-flowing metal to adopt a variety of lead thread profiles.

Some lead thread profiles are particularly susceptible to false threads. In some cases, the profile of the lead thread varies too much along the length of the lead thread to cause false threading. For example, the lead thread can rise in height too fast, that is, it grows from the axis to the full height of a standard thread by less than 180 ° around the axis. For another example, the flat angled leading flank angle of the lead thread may be too steep to allow proper engagement with female threads. As a further example, the lead thread profile can be very pointed, which can lead to possible false threading and / or unintended and unwanted contact with internal female threads during initial threading. For anti-cross thread fasteners, some lead thread profiles may cause the anti-cross thread clamp to make a false thread on the internal female threads before the anti-cross thread has a chance to align the joint members. clamping for a correct threading. Some lead thread profiles cause the internal and external threads to contact each other at an undesired location on the respective helixes, before the anti-cross thread acts on the internal thread to align the clamping members, thereby hindering and / or preventing the anti-cross thread from rising over the internal lead thread of the female clamping member. This can be especially true when the initial angular misalignment of the two clamping members is high. Additionally, many lead thread profiles on an external male clamping member can engage a slot in the internal female cable to cause a false thread condition, as described above.

Some lead threads used in anti-cross thread fasteners have a steep helix angle, such that the lead thread grows from zero height to anti-cross thread height by only 270 ° around the axis. Spikes on short lead threads such as these can engage the lead thread groove of female internal fasteners and / or the smaller groove of internal full threads, leading to false threading.

In other lead threads used over anti-cross thread fasteners, the lead thread profile width is constantly maintained to be similar to the standard thread width, as the lead thread height increases throughout. length of lead thread length. These lead threads tend to form a profile, which is different in each section of the lead thread. They tend to have a very flat curve near the start of the lead thread, and a progressively smaller, more pointed profile as the lead thread helix progressively blends into the anti-cross thread profile. These lead threads tend to lodge in the groove at the tip of the internal female lead thread as the lead thread grows in height, leading to false threading.

What is needed, therefore, is an external lead thread of a male clamp member which tends to prevent false threading of the lead thread into a groove in the peak of the internal thread of a female clamp member. The lead thread should not be subject to manufacturing variations that cause undesirable localized lead thread heights and profiles and large helix angles. For anti-cross thread fasteners, a leading thread is needed that will facilitate, rather than hinder, the performance of the anti-cross thread. This and other objects can be achieved by an anti-false threaded fastening system as defined in the independent claims. Other improvements are characterized in the dependent claims.

The fasteners, fastener systems and procedures to prevent or resist false threading are disclosed.

One embodiment of the invention provides an anti-false threaded fastening system comprising: a female clamping member comprising: at least one female clamping thread formed within the female clamping member; at least one female lead thread formed within the female clamp member; a male clamping member comprising: a shaft having a leading end for insertion within the female clamping member; at least one male clamp thread formed on the outside of the shaft as a plurality of thread windings adapted to mate with the female clamp thread; at least one male lead thread formed on the outside of the shaft at the leading end that is at least half a wrap around the shaft and comprises a curved profile defined by an arc having a radius approximately equal to a radius of an arc that is tangent to both flanks of a thread profile of the at least one male clamping thread and below the pitch line of the at least one male clamping thread.

Another embodiment provides an anti-false threaded fastening system comprising: a female clamping member comprising: at least one female clamping thread formed within the female clamping member; at least one female lead thread formed within the female clamp member; a male clamping member comprising: a shaft having a leading end for insertion within the female clamping member; at least one male clamp thread formed on the outside of the shaft as a plurality of thread windings adapted to mate with the female clamp thread; at least one male lead thread formed on the outside of the shaft at the leading end that is at least half a wrap around the shaft and is shorter at one lead end of the male lead thread wrap and taller at the other end of the male lead thread winding, wherein the at least one male lead thread comprises an apex having a height that changes at a substantially constant rate between the ends of the male lead thread winding, and wherein the male thread It comprises a male lead thread flank which is anchored to the root of an adjacent thread winding along the entire length of the male lead thread.

Still another embodiment provides an anti-false threaded fastening system comprising: a female clamping member comprising: at least one female clamping thread formed within the female clamping member; at least one female lead thread formed within the female clamp member; a male clamping member comprising: a shaft having a leading end for insertion within the female clamping member; at least one male clamp thread formed on the outside of the shaft as a plurality of thread windings adapted to mate with the female clamp thread; at least one male lead thread formed on the outside of the shaft at the leading end which is at least half a wrap around the shaft, wherein at least one male lead thread is shorter at a leading end of the thread winding of male lead and tallest at the other end of the male lead thread winding, wherein the male lead thread comprises a profile having a height and shape adapted to resist false threading in a groove at the apex of a thread. female attack within a female clamping member.

The above and other preferred features, including various novel implementation details and element combination, will now be more particularly described with reference to the accompanying drawings and will be pointed out in the claims. It will be understood that the particular procedures and circuits described herein are shown by way of illustration only and not as limitations.

The accompanying figures, which are included as part of the present specification, illustrate the various embodiments of the system and method currently disclosed and, together with the general description given above and the detailed description of the embodiments given below, serve to explain and teach the principles of present bras, bra systems, and bra procedures.

Figure 1 illustrates a side view of a prior art male clamping member with a standard thread, identifying various parts of the standard thread, including "apex, flank, root, pitch, thread angle, minor diameter and larger diameter.

Figure 2 illustrates a side view of prior art male and female fastener members with misaligned longitudinal axes, which is a condition for possible cross-threading with prior art fasteners.

Figures 3A and 3B show side views of prior art male and female fastening members, which are translationally misaligned with each other so as to be out of step for possible false threading of fasteners, in which figure 3B is a close-up view relative to Figure 3A.

Figures 4A-4F illustrate cross-sectional side views and an end view of a prior art female clamp member having a female lead thread on the inside of the female clamp member, wherein the lead thread female has a groove at its vertex.

Figures 5A and 5B show side views of a prior art male clamping member having a pointed lead thread.

Figure 6 illustrates a side view of a prior art male clamping member having a pointed lead thread that blends into an anti-cross thread.

Figure 7 shows a side view of a prior art male clamping member with an entry point and a pointed lead thread that blends into an anti-cross thread.

Figures 8A-8C show side views of a prior art fastener blank that is wound between dies and illustrate how a lead thread is typically formed in a fastener by allowing metal in a fastener blank to fill. only partially a groove in the die so that the lead thread is a free form.

Figures 9A and 9B, in which Figure 9B is a close-up view, illustrate side views of a male clamping member of the present invention having: a head and a shaft in which the shaft has a clamping thread, an anti-cross thread, and a lead thread on the same propeller.

Figures 10A-10E illustrate cross-sectional side views and an end view of a male clamp member of the present invention having an anti-cross thread and a lead thread on the same helix, wherein the lead thread It is anchored to the anti-cross thread.

Figures 11A-11E illustrate cross-sectional side views and an end view of a male clamp member of the present invention having a clamp thread and a lead thread on the same helix, wherein the lead thread is anchored to the next winding.

Figures 12A-12E illustrate cross-sectional side views and an end view of a male clamp member of the present invention having an anti-cross thread and a lead thread on the same helix, wherein the lead thread It is not anchored to the anti-cross thread and is in the middle of a clamping thread profile.

Figures 13A-13E illustrate cross-sectional side views and an end view of a male clamp member of the present invention having a clamp thread and a lead thread on the same helix, wherein the lead thread does not it is anchored to the next winding and is as far away from the next winding as possible while still within a clamping thread profile.

Figures 14A-14E show cross-sectional side views of a male clamp member of the present invention in place within the female clamp, wherein the male lead thread of the male clamp member passes over a groove at the apex of the female lead thread to resist or prevent false threading.

Figure 14F is an end view of a female clamp member having a lead thread.

Figures 15A-15C show a side view of a male clamp member of the present invention having an entry point at the leading end of the shaft.

Figures 16A-16D illustrate cross-sectional side views of male fasteners having entry points.

The figures are not necessarily drawn to scale, and elements of similar structures or functions are generally represented by like reference numerals for illustrative purposes throughout the figures. The figures are only intended to facilitate the description of the various embodiments described herein. The figures do not describe all aspects of the teachings disclosed herein.

In accordance with the teachings of this disclosure, the present invention satisfies the aforementioned need and also overcomes other shortcomings and deficiencies of existing fastener technologies by providing a novel start to the thread helix (also referred to as the 'lead thread' of a threaded fastener), an anti-false thread that aligns a lead thread, the unique contour of which is such that it does not penetrate deeply and / or remain in the grooves present in the nose of the lead thread, and / or full thread , of the internally threaded helix of a female clamping member. The lead thread with an anti-false thread contour may be present on the clamp for approximately one and one fifth turns of the helix, whereby it maintains essentially the same broadly curved peak profile in each axial section of the thread. attack.

Figures 9A and 9B illustrate an embodiment of the present invention, in which Figure 9B is a close-up view of the leading end portion of the clamp shown in Figure 9A. As shown in Figures 9A and 9B, the clamping comprises both an anti-cross thread and a lead thread that prevent false threading. The male clamping member 10 of this embodiment is a bolt or screw having a helix of threads 11 externally wound on the shaft 12 of the male clamping member 10. A head 13 is formed at one end of the shaft 12 of the male clamping member. 10 and is adapted to be engaged by means of applying a rotational torque. Head 13 may be slotted to receive a flat, Phillips, Torx, or screwdriver-like blade, or it may have a plurality of surfaces for engagement by a wrench, socket, Allen, or other means for rotationally engaging the head. Head 13 may take any shape known in the art to impart rotational engagement to the clamp. The male clamping shaft may also be connected to a portion of the device to be clamped, such as by welding or other means, so that a female clamping member can be rotationally threaded thereon for clamping. In this case, the feature connected to a portion of the device to be clamped is the head of the male clamping member.

The helix of threads 11 wound around the axis 12 of the male clamping member 10 can adopt several distinctly different profiles along its length, as it advances around the axis 12 from the head 13 to the leading end 14 of the clamping . These various thread profiles are described with reference to Figures 9A and 9B. Adjacent to the head 13 there may be a number of clamping thread windings 15, such as those found in a standard fastener (see Figure 1). These threads can be followed, while the helix 11 is wound away from the head 13, by a short section of anti-cross threads 16, in which the clamping thread 15 mixes with the anti-cross thread 16 on the same helix 11 The anti-cross thread 16 has a profile that imparts the anti-cross thread function to that section of the helix, since at least a portion of a turn of the thread helix has a surface that is transiently curved from the minor diameter to the diameter. higher. A detailed description of an anti-cross thread 16 is provided in US patent 5,730,566. The anti-cross thread 16 can be followed on the helix 11 by the lead thread 17. All these thread profiles, regardless of their shape Localized specific contours and contours are contained within the envelope defined by the profile of a clamping thread 15.

In an alternative embodiment of a male clamping member, the thread helix 11 comprises a clamping thread 15 and a leading thread 17, without an anti-cross thread, such that the clamping thread 15 blends directly with the lead thread 17.

As shown in Figure 9B, lead thread 17 begins at the location on helix 11 where lead thread 17 meets anti-cross thread 16 at mixing point 18 and extends the rotations of one and one. one-fifth around helix 11 to helix termination point 19. At mixing point 18, lead thread 17 reaches its highest or highest point, measured from the thread axis, and has a height and a profile matching that of anti-cross thread 16. From mixing point 18, lead thread 17 follows helix 11 for one and a fifth turn around male clamping member 10 and away from head 10, until The lead thread 17 terminates at the termination point of the helix 19. The lead thread height, measured from the roots of the lead thread 15, decreases at an essentially constant rate over its entire length as winds around the clamping body towards the leading end 14 of the member or male clamp 10. In one embodiment, the rate of decrease in the height of lead thread 17 is neither significantly greater nor significantly less than a rate of decrease calculated using a length of approximately one and a fifth turn of the helix, until its height and width reach essentially zero at the termination point of the helix 19 at the height of the root of the clamping thread 15 (minimum diameter).

From the leading end 14 of the male clamping member 10, the leading thread 17 may start at zero height in a cylinder of a diameter defined by the root of the clamping thread 15. The apex of the peak of the clamping thread 15. The lead can start at the root height of the standard thread, then when the lead thread is wound around the clamp body towards the head 13, its peak may diverge from the root height and propeller axis of the clamping, at a constant rate, such that the peak grows in height from essentially zero at its beginning to a height slightly less than the pitch line of the standard thread, which is approximately the height of the anti-cross thread 16, at blend point 18. During this height increase, the width of the lead thread profile gradually increases as the lead thread advances around the body of the clamp.

In one aspect of the current invention, the leading thread of the anti-false thread may be shaped such that the height of the thread increases at a designated maximum constant rate as it advances around the body of the fastener from the beginning of the propeller until it mixes with the next section of the propeller. In alternative embodiments, the lead thread may extend around the axis for any number of turns of the helix, but at least half a winding around the axis, as long as the rate of rise does not present a steep point at the apex of the lead thread. which could become falsely threaded into a female clamping member. The rate of increase can be such that the included helix taper angle of the external lead thread profile peak is consistent and does not exhibit a severe angled surface, bumps, sharpness, or other inconsistent characteristics that can easily enter any groove. at the peak of the lead thread of the normal internal thread helix when the external lead thread is presented to the receiving internally threaded member at any normal angle of assembly. As such, when the peaks that form the respective apexes of the mating lead threads of the two members come into contact at any point during assembly, the peak of the outer clamp does not increase in height at such a rapid rate that it grows in height. any grooves in the internal peak (and prevents further progression of the two threaded helices relative to each other) before the two peaks slide over each other due to axial load applied by the installer. The outer profile of the lead thread allows the two lead threads to contact each other and then slide over each other without binding and / or binding the two threads as the fasteners rotate in the assembly.

In another aspect of the current invention, the lead thread can have a constant profile in each axial section of the helix and the profile can be essentially non-pointed, broad curve, or series of planes and / or curves that approximate a curve. smooth of the designated radius, essentially invariable in the profile of the peak along the length of the lead thread, such that, in case of undesirable contact with the groove present in the peak of the internal thread of a clamping member female, the external thread spike of a male clamping member may not easily enter any such groove, nor may it have an increasingly pointed or inconsistent spike in the groove of the internal thread as it rotates when it comes into contact with the groove. of the internal thread. Being configured in this way, the lead thread of the male clamping member cannot thread into or become lodged in any groove present in the nose of the lead thread of the receiving helix, thereby avoiding false threading or otherwise interfering. with the necessary axial realignment that takes place due to transverse anti-cross thread movement of the adjacent transverse anti-cross thread section of the helix.

In another aspect of an embodiment of the invention, the peak of the external lead thread of a male clamping member forms an essentially non-helical annular ring, within a standard thread profile helix path wrap around the body of the clamping. Thus, when presented to the helically shaped beak of an internal lead thread of a female clamp member, the beak of the external lead thread of a male clamp member extends through the slot into a beak of the internal drive thread. When the clamping members are rotated relative to each other, the peak of the external lead thread of a male clamp member passes through and does not screw into the groove in the peak of the internal lead thread of the female clamp member.

Embodiments of the present invention can avoid false threading when an externally threaded member engages an internally threaded member. Embodiments of the invention can avoid cross-threading when an externally threaded member engages an internally threaded member. Embodiments of the invention can correct for linear misalignment (non-collinearity) between two members that can be threaded together and have mating helical threads. Embodiments of the invention can correct for angular misalignment (non-angular collinearity) between two members that can be threaded together and have mating helical threads. Embodiments of the invention correct for angular misalignment between a first clamping member and a second clamping member by having one or more cam threads of the first member over the threads of the second member, thereby bringing the first and second members to an angularly collinear alignment.

Embodiments of the invention correct for linear misalignment between a male clamping member and a female clamping member by providing an external lead thread of the male clamping member that connects any grooves present in the peak of an internal thread of the female clamping member while slides along the beak and across the groove edges of the female clamp member, in the process of bringing the male and female members into collinear and / or collinear alignment.

Some embodiments of the invention minimize inadvertent contact of externally threaded helix lead thread sections with the internally threaded helix peak, during camming of an anti-cross thread within fasteners. The lead thread may have a lead thread profile consisting of various cross sections of the lead thread. The lead thread can have a constant maximum growth rate from its termination point on the clamping shaft to the point where it mixes with the next thread form, if the next thread form is an anti-cross thread, a standard thread, or any other known thread form.

Some embodiments of the invention have a protruding diameter feature at the forward end of the male clamping member, such as an attack point or a dog point, which restricts the misalignment angle between male and female members.

One design consideration of the fastener is to maintain the length of the design wrap for the fastener while adding anti-cross thread and anti-false thread features to the fastener. Embodiments of the invention include lead threads that reduce false threading, anti-cross threads, and dog tips, without exceeding the design wrap for the length of the clamp.

In one aspect of the present invention, the lead thread of a male clamp member cannot be false thread on the internal thread helix of a female clamp member by keeping its external lead thread peak (center) as close as possible from the root of the thread adjacent to the lead thread. In this way, the lead thread forms an essentially non-helical thread within the shell of the normal external thread helix, thereby allowing the lead thread to deliberately cross any helical groove of the internal thread peak without catching or threading. false in the groove.

Some aspects of the present invention can prevent the lead thread section of a helix from interfering during thread lift of an adjacent anti-cross thread section of the helix. Interference can be avoided when the lead thread has an essentially constant growth rate and the lead thread has a thread profile that blends smoothly with the profile of the adjacent anti-cross thread, so that the lead thread withstands any additional cam that may be required to assist the anti-cross thread to achieve its normal function of aligning the clamping members.

Certain embodiments of the invention can eliminate interference of the lead thread of a male clamp member with the peak of the internal thread of a female clamp member during camming of an anti-cross thread. Interference can be eliminated by a wide, consistent, fully formed curved lead thread profile that constantly changes in height, width and profile along the lead thread.

Depending on the length of the lead thread on a male clamping member, it may deliberately present a constant maximum thread height at its potential point of contact with the peak of the internal thread to avoid undesirable contact of the lead thread with the lead thread. internally threaded helix peak when the male clamping member is inserted into the female clamping member.

Figure 10E shows an end view of an anti-cross thread fastener having a lead thread of the present invention. The leading end 14 of the male clamping member 10 is clearly visible in this view. The outer periphery of the leading end 14 is defined by the standard root diameter 20. From the termination point of the helix 19, the leading thread 17 grows in height as it winds around the clamp one and one-fifth turns. in a clockwise direction until it mixes with the anti-cross thread 16 at the mixing point 18. The apex of the lead thread 21 grows in height at a constant rate. The apex of anti-cross thread 21 is mostly constant in height until it grows to mix with the clamping thread 15 at the mixing point 28. The apex of the clamping thread 23 has the greatest height.

Figure 10A illustrates a cross-sectional view of the threads taken at A-A in Figure 10E. In Figure 10A, two turns of lead thread 17 are shown adjacent to one turn of anti-cross thread 16. The shortest turn of lead thread 17, shown to the left of Figure 10A, is approximately 1 / 6 of its total height. The highest winding of lead thread 17, shown in the middle of Figure 10A, is its full height because it is at the mixing point 18 with anti-cross thread 16, in which both the total height of the thread lead 17 and the height of the anti-cross thread 16 are slightly shorter than the pitch diameter 24 of the clamping thread 15 (not shown in FIG. 10A). For purposes of illustration, a clamp thread profile 25 is shown by a dotted line superimposed on the topmost winding of lead thread 17 so that the relative sizes and profiles can be readily apparent.

In this embodiment, lead thread 17 has a broadly curved profile as it advances around thread helix 11. Lead thread 17 maintains an essentially constant radially curved surface from root to root through its apex 17c. The vertex 17c of its profile in any axial section is the highest point on a curve of essentially the same radius R in that section. The radius R of the curve defining the lead thread profile is determined by extending the curve from each root at points that would be essentially tangent to the imaginary flanks of a standard thread profile superimposed on the lead thread profile. This is done where the lead thread 17 is highest, that is, at the mixing point 18, where the height of the lead thread 17 is just below the pitch line 24 of the clamp. Radius R remains essentially constant along the length of lead thread 17, as the height of the thread profile decreases as it extends from blend point 18 to helix termination point 19, so that the lead thread 17 has the same curvature as its profile in all sections. As such, the width of lead thread 17 is at its maximum at mixing point 18 and decreases as its height decreases, until its width is zero at the propeller termination point 19.

Lead thread 17 of the embodiment shown in Figures 10A-10E also maintains its proximity to the root that it shares with anti-cross thread 16. As lead thread 17 becomes smaller as it is wound around of the clamping from the mixing point 18, remains essentially anchored to the root of the adjacent anti-cross thread 16 of the helix 11.

Figure 10A illustrates a cross-sectional view of the threads taken at A-A in Figure 10E. At mixing point 18, the median line extending vertically through radially curved lead thread 17 is located on the vertical center line of the clamp thread profile 25, which is also the center line of the anti thread. -cross 16 at blending point 18. As lead thread 17 winds around clamping toward the termination point of helix 19, the vertical median line of lead thread profile diverges from the center line vertical of the profile of the clamping thread 25 and gradually approaches the root of the thread of the adjacent anti-cross thread 16 for one complete turn and approaches the root of the thread that it shares with itself for another fifth turn of the Thread-drive propeller. At the termination point of helix 19, the median line of lead thread 17 roughly intersects the median of the adjacent root. At the termination point of the helix 19, the profile of the lead thread 17 is reduced such that its height and width have reached essentially zero, while its position axially on the male clamping member 10 has reached approximately the root. of the adjacent winding of the lead thread 17. This has the effect of anchoring the root 17b of the lead thread 17 to the root of the adjacent thread, while the opposite root 17a of the lead thread 17 emerges from the opposite root of the profile 25 of the clamping thread and gradually approaches the root of the adjacent anti-cross thread 16. In this way, the apex of the lead thread 17c forms an essentially annular ring around the male clamping member 10, within of the wrapping of the helix path of the clamping thread profile 25.

Figure 10D illustrates a cross-sectional view of the threads taken at D-D in Figure 10E. In this position around the male clamping member 10, the lead thread 17 is adjacent to the anti-cross thread 16 so that the root 17b of the lead thread is shared with the root of the anti-cross thread 16. A clamp thread profile 25 and an anti-cross thread profile 26 are shown in dotted lines and overlap on lead thread 17 so that the relative sizes and profiles are readily apparent. In this position, lead thread 17 is approximately 79% of its greatest height. The radius R of the curve defining the profile of the lead thread 17 from the root 17a through the apex of the lead thread 17c to the other root 17b is the same as the radius of the curved profile of the lead thread at the mixing point shown in Figure 10A. The root of the lead thread 17b continues to share with the root of the anti-cross thread 16, while the root 17a of the opposite lead thread has moved from a position similar to where the root of the lead thread would be as indicates the profile of the overlapping clamping thread 25.

Figure 10C illustrates a cross-sectional view of the threads taken at C-C in Figure 10E. In this position around the male clamping member 10, the lead thread 17 is adjacent to the anti-cross thread 16 so that the root 17b of the lead thread is shared with the root of the anti-cross thread 16. A clamp thread profile 25 and an anti-cross thread profile 26 are shown in dotted lines and overlap on lead thread 17 so that the relative sizes and profiles are readily apparent. In this position, lead thread 17 is approximately 58% of its greatest height. The radius R of the curve defining the profile of the lead thread 17 from the root 17a through the apex of the lead thread 17c to the other root 17b is the same as the radius of the curved profile of the lead thread at the mixing point shown in Figure 10A. The root of the lead thread 17b continues to share with the root of the anti-cross thread 16, while the root 17a of the opposite lead thread has been further displaced from a position similar to where the root of the lead thread would be. as indicated by the profile of the overlapping clamping thread 25.

Figure 10B illustrates a cross-sectional view of the threads taken at B-B in Figure 10E. In this position around the male clamping member 10, the lead thread 17 is adjacent to the anti-cross thread 16 so that the root 17b of the lead thread is shared with the root of the anti-cross thread 16. A clamp thread profile 25 and an anti-cross thread profile 26 are shown in dotted lines and overlap on lead thread 17 so that the relative sizes and profiles are readily apparent. In this position, lead thread 17 is approximately 37% of its greatest height. The radius R of the curve defining the profile of the lead thread 17 from the root 17a through the apex of the lead thread 17c to the other root 17b is the same as the radius of the curved profile of the lead thread at the mixing point shown in Figure 10A. The root of the lead thread 17b continues to share with the root of the anti-cross thread 16, while the root 17a of the opposite lead thread has been further displaced from a position similar to where the root of the lead thread would be. as indicated by the profile of the overlapping clamping thread 25.

Referring again to Figure 10A, a shorter portion of lead thread 17 is visible on the left side of the figure. Because lead thread 17 extends one and a fifth turn of the helix, two windings of lead thread 17 are visible in Figure 10A: the full height winding of lead thread 17 is in the middle of the figure; and the nearly completed winding of lead thread 17 is on the left side of the figure. Root 17b of the nearly completed wrap is shared with root 17a of the full-height wrap of lead thread 17. Even at this low height, lead thread 17 of the nearly completed wrap has a curved profile that has a radius R which is the same as the radius of the curved profiles in the other positions.

The embodiment of the invention illustrated in Figures 10A-10E has a lead thread 17 that combines: a curved profile, a constant maximum rate of change in peak height, and a non-helical wrap around the clamping axis. These features combined may allow the lead thread 17 to slide along and over the lead thread of an internally threaded female member (not shown) without engaging any depressions and / or grooves in the peak of the internal female lead thread. . The lead thread 17 of the male clamping member 10 may thus allow the adjacent anti-cross thread 16 to more effectively correct any angular or axial misalignment with an internally threaded female member (not shown) so that cross-threading can be avoided. and / or false threading.

Figures 11A-11E illustrate another embodiment of a male clamping member having a lead thread. Figure 11E is a view of the leading end 14, and Figures 11A-11D are cross-sectional views taken in an axial direction at the positions indicated in Figure 11E. This male clamp member 10 has windings of a clamping thread 15 and more than two and a fourth winding of a lead thread 17. As shown in Figure 11E, lead thread 17 begins at a helix termination point. 19 where its height is zero and it grows in height as it is wound around the shaft until it reaches its full height at the mixing point 18 where the lead thread 17 mixes with the clamp thread 15.

Figure 11A illustrates a cross-sectional view of the threads taken at A-A in Figure 11E. Referring to Figure 11A, a shorter portion of lead thread 17 is visible on the left side of the figure. Because lead thread 17 extends for more than two and one-quarter turns of the helix, three turns of lead thread 17 are visible in Figure 11A: a shorter turn to the left, a middle turn to the left. the middle and higher curl on the right. As the lead thread 17 winds around the clamp from the termination point of the helix 19, it becomes taller and remains anchored to the root that it shares with the median winding of itself for one complete turn of the helix. thread of attack. At the termination point of helix 19, lead thread 17 roughly intersects the median of the adjacent root. At the termination point of the helix 19, the profile of the lead thread 17 is reduced such that its height and width are essentially zero, while its position axially on the male clamping member 10 is approximately at the root of the adjacent winding of the lead thread 17. This has the effect of anchoring the root 17b of the lead thread 17 to the root of the adjacent winding, while the opposite root 17a of the lead thread 17 has come off the opposite root of the lead thread 17. profile of the clamping thread 25 (shown by dotted lines) and gradually approaches the anchored root 17b. In this way, the apex of the lead thread 17c forms an essentially annular ring around the male clamp member 10, within the envelope of the helix path of the clamp thread profile 25. In cross section AA, the winding The shortest lead thread is approximately 8.3% of the total height, the medium lead thread winding is approximately 52.7% of the total height, and the highest lead thread winding is approximately 97 , 2% of the total height.

Figure 11B illustrates a cross-sectional view of the threads taken at B-B in Figure 11E. In this position around the male clamping member 10, the shorter winding of the lead thread 17 is adjacent to the highest winding of the lead thread 17 so that the shorter root 17b of the lead thread is shared with the highest root of lead thread 17a. The clamping thread profiles 25 are shown in dotted lines and are superimposed on the lead thread windings 17 so that the relative sizes and profiles can be readily apparent. In cross section B-B, the shortest lead thread winding is approximately 19.4% of the total height, and the highest lead thread winding is approximately 63.9% of the total height. The radius R of the curve defining the profile of the shortest winding of lead thread 17 from root 17a through the apex of lead thread 17c to the other root 17b is the same as the radius of an arc ( similar to the anti-cross thread profile 26) that will extend from the root following the clamping thread profile 25. The root of the leading thread 17b of the shortest winding continues to share with the root 17a of the highest winding of the thread of lead thread 17, while the root 17a of the opposite lead thread has moved from a position similar to where the root of the standard thread would be as indicated by the profile of the overlapping clamp thread 25.

Figure 11C illustrates a cross-sectional view of the threads taken at C-C in Figure 11E. In this position around the male clamping member 10, the shorter winding of the lead thread 17 is adjacent to the higher winding, so that the root of the lead thread 17b of the shorter winding is shared with the root 17a of the Highest lead thread winding 17. The clamping thread profiles 25 are shown with dotted lines and are superimposed on the lead thread windings 17 so that the relative sizes and profiles can be readily apparent. In cross section C-C, the shortest lead thread winding is approximately 30.5% of the total height, and the highest lead thread winding is approximately 75.0% of the total height. The lead thread profile may comprise a curved surface having a radius R equal to the radius of an arc (similar to anti-cross thread profile 26) that would extend from root to root of clamping thread profile 25 .

Figure 11D illustrates a cross-sectional view of the threads taken at DD in Figure 11E. In this position around the male clamping member 10, the shorter winding of the lead thread 17 is adjacent to the higher winding, so that the root of the lead thread 17b of the shorter winding is shared with the root 17a of the uppermost winding of the lead thread 17. The clamping thread profiles 25 are shown with dotted lines and are superimposed on the lead thread windings 17 so that the relative sizes and profiles can be easily obvious. In cross section DD, the shortest lead thread winding is approximately 41.7% of the total height, and the highest lead thread winding is approximately 86.1% of the total height. The top wrap lead thread profile may comprise a combination of curved and straight surfaces depending on the configuration of the rolling dies used to make the lead thread. In particular, the top wrap lead thread profile may comprise a combination of an anti-cross thread and a standard thread as shown in Figure 11D. The shortest turn of the lead thread may have a bend with a radius that is the same as the radius of an arc (similar to anti-cross thread profile 26) that would extend from root 17a to root 17b.

Figures 12A-12E illustrate another embodiment of a male clamping member having a lead thread. Figure 12E is a view of the leading end 14, and Figures 12A-12D are cross-sectional views taken in an axial direction at the positions indicated in Figure 12E. This male clamping member 10 has windings of a lead thread 17, an anti-cross thread 16, and a clamp thread 15. As shown in Figure 12E, the lead thread 17 begins at a helix termination point 19 where its height is zero and it grows in height as it is wound around the axis until it reaches its full height at the mixing point 18, where the lead thread 17 mixes with the anti-cross 16.

Figure 12A illustrates a cross-sectional view of the threads taken at A-A in Figure 12E. Referring to Figure 12A, a shorter portion of lead thread 17 is visible on the left side of the figure. Because lead thread 17 extends over the helix turn, two turns of lead thread 17 and one roll of anti-cross thread 16 are visible in Figure 12A: a shorter turn of thread lead 17 to the left, a higher turn of the lead thread 17 in the middle and an anti-cross thread roll to the right. As the lead thread 17 winds around the clamp from the termination point of the helix 19, it becomes taller, but in this embodiment, it does not remain anchored to the root of the adjacent winding itself. At the termination point of the helix 19, the lead thread 17 is approximately in the middle position of the clamp thread profile 25 (shown in dotted line and overlaps the lead thread 17). At the termination point of the helix 19, the profile of the lead thread 17 is reduced such that its height and width are essentially zero, while its position axially on the male clamping member is separate and apart from the root. of the adjacent lead thread winding 17. In cross section AA, the shortest lead thread winding is approximately 16.7% of the total height, the highest lead thread winding is approximately 95% of the total height for the lead thread 17, and the anti-cross thread 16 is its maximum height. As shown in Figures 12A and 12E, lead thread 17 is at full height at mixing point 18, where it mixes with anti-cross thread 16. As shown in Figure 12E, anti-cross thread -Cross 16 is mixed with the clamping thread 15 at a second mixing point 28.

Figure 12B illustrates a cross-sectional view of the threads taken at B-B in Figure 12E. In this position around the male clamping member 10, the lead thread 17 does not share a root with the adjacent anti-cross thread 16 because there is a space separating them. A clamp thread profile 25 is shown in dotted lines and overlaps the lead thread wrap 17 so that the relative sizes and profiles can be readily apparent. In cross section B-B, the lead thread is approximately 37.5% of its total height. The radius R of the curve that defines the profile of lead thread 17 from root 17a through the apex of lead thread 17c to the other root 17b is the same as the radius of an arc (similar to the profile of anti-cross thread 26) that will extend from the root following the clamping thread profile 25.

Figure 12C illustrates a cross-sectional view of the threads taken at C-C in Figure 12E. In this position around the male clamping member 10, the lead thread 17 does not yet share a root with the adjacent anti-cross thread 16. A clamp thread profile 25 is shown in dotted lines and overlaps the lead thread windings 17 so that the relative sizes and profiles can be readily apparent. In cross section CC, the lead thread is approximately 58.3% of the total height of lead thread 17. The lead thread profile may comprise a curved surface having a radius R equal to the radius of a arc (similar to anti-cross thread profile 26) that would extend from root to root of clamping thread profile 25.

Figure 12D illustrates a cross-sectional view of the threads taken at D-D in Figure 12E. In this position around the male clamping member 10, the lead thread 17 is still spaced from the adjacent anti-cross thread 16. A clamp thread profile 25 is shown in dotted lines and overlaps the lead thread 17 , so that relative sizes and profiles are easily apparent. In cross section D-D, the shortest lead thread is approximately 79.2% of the total height. The lead thread profile may have a curve with a radius that is the same as the radius of an arc (similar to anti-cross thread profile 26) that would extend from root 17a to root 17b.

Figures 13A-13E illustrate another embodiment of a male clamping member having a lead thread. Figure 13A illustrates a cross-sectional view of the threads taken at AA in Figure 13E. Referring to Figure 13A, a shorter portion of lead thread 17 is visible on the far left side of the figure. Because the lead thread 17 extends for more than two and a quarter turns of the propeller, three windings of lead thread 17 are visible in FIG. 13A: a shorter wrap on the far left, a medium wrap in the middle, and a higher wrap on the right. As the lead thread 17 winds around the clamp from the termination point of the helix 19, it becomes taller and remains as far away as possible from the median winding of itself for one complete turn of the helix thread. while the small winding remains within a clamping thread profile 25 (shown in a dotted line superimposed on the lead thread. Figure 13B illustrates a cross-sectional view of the threads taken at BB in figure 13E. In this position around male clamping member 10, the shortest winding of lead thread 17 is as far as possible from the adjacent highest winding of lead thread 17. Figure 13C illustrates a cross-sectional view of the threads taken in CC in Figure 13E. In this position around the male clamping member 10, the shortest winding of the lead thread 17 is still as far from the winding as possible. adjacent uppermost recess of lead thread 17, while remaining within a clamp thread profile 25 (shown in dotted line superimposed on lead thread). Figure 13D illustrates a cross-sectional view of the threads taken at DD in Figure 13E. In this position around male clamping member 10, the shorter wrap of lead thread 17 does not yet share a root with the adjacent higher wrap.

In some embodiments of the invention, over the entire length of the lead thread, approximately one and a fifth turn of the helix, its profile can be a curve at its peak, in which the curve has the same radius in each axial section. , such that in any section its profile effectively bridges any groove present in the internal lead thread of a female clamping member.

While alternative embodiments of the lead thread do not have a height that grows at a constant rate as it is wound around the axis of the clamp, one aspect of the lead thread of the invention is that it does not have localized protrusions, points , or sudden increases in the height or contour of the lead thread that could jam and continue to thread into the groove in the peak of an internal lead thread of a female clamp member. Some embodiments of the invention have a lead thread that has a constant growth rate along with a uniform profile, which prevents the anti-false lead thread from entering any groove present in the internal lead thread of a clamping member. female. Embodiments of the invention have a lead thread profile to further allow the lead thread to slide over any grooves present in the internal lead thread of a female clamp member with minimal applied axial force. Thus, the male clamping member cannot be threaded or gripped against any spike grooves of the female clamping member.

Figures 14A-14F show cross-sectional views and an end view of a female clamp member having an internal lead thread and a corresponding male clamp member inserted therein, but without any relative rotation of the legs. members. The female clamping member 30 having an internal lead thread 31 is the same as illustrated in Figures 4A-4F. As shown in Figures 14A-14E, which are cross-sectional views of the threads at the positions identified in Figure 14F, the male clamping member 10 can be inserted into the female clamping member without rotational movement. Before the members rotate relative to each other to engage the threads, the lead thread 17 of the male clamp member 10 bridges the different depths of the groove 32 at the peak of the internal lead thread 31 of the female clamp member 30 , without entering it into any section of slot 32.

Figures 15A-15C show side views of male clamping members of the present invention having a lead thread and various entry points. The helix of threads 11 wound around the axis 12 of the male clamping member 10 can assume several distinctly different profiles along its length, as it advances around the axis 12 from the head (not shown) to the leading end 14 of the clamping. Male clamping member 10 may have multiple clamping thread windings 15, wherein clamping thread 15 may be a standard thread (see Figure 1) or any other thread known to those skilled in the art. The clamping thread 15 can be followed, as the helix 11 is wound towards the leading end 14, by a short section of anti-cross thread 16, in which the clamping thread 15 mixes with the anti-cross thread. cross 16 on the same helix 11. The anti-cross thread 16 has a profile that imparts the function of anti-cross thread to that section of the helix, since at least a portion of a winding of the thread helix has a surface transiently curved from the smallest diameter to the largest diameter. A detailed description of an anti-cross thread 16 is provided in US Patent 5,730,566. The anti-cross thread 16 may be followed on the helix 11 by the lead thread 17 as described in detail with reference to Figures 10A. -10E. These thread profiles, regardless of their specific localized shape and profile, may be contained within the envelope defined by the profile of a clamping thread 15. At the leading end 14, an entry point 50 is formed in the clamping member. male clamp 10. A detailed description of an entry point 50 is provided in US Patent 6,062,786. In Figure 15A, the entry point 50 tapers from a larger diameter in lead thread 17 to a smaller diameter. at the tip. In Figure 15B, the entry point 50 is a cylindrical shape with a diameter slightly greater than the minimum diameter of the clamping thread 15. In Figure 15C, the entry point 50 is a cylindrical shape with a diameter slightly less than the minimum diameter of the clamping thread 15. In other embodiments, any entry point known to those skilled in the art may be formed at the leading end of the male clamping member. Still other embodiments may comprise an entry point having a diameter greater than the minimum diameter at the root of the lead thread and / or the clamp thread. When adding a larger diameter entry point to a male clamping member, the lead thread can be relatively shorter when the rate of change of lead thread height is the same. A relatively shorter lead thread can be the result of the lead thread ending on a higher surface, that is, the entry point with the largest diameter.

The minimum diameter of the lead thread 17 can be smaller or larger than the minimum diameter of an anti-cross thread 16 or a clamp thread 15. For example, as shown in Figure 15, the entry point 50 may have an outer diameter greater than the minimum diameter of the clamping thread 15. The minimum diameter of the lead thread 17 may be greater at the termination point of the helix 19, and the minimum diameter of the lead thread 17 may be reduced as the lead thread is wound around the shaft to the mixing point 18, and each winding of lead thread 17 can be further reduced, through an anti-cross thread 16 until the minimum diameter of the lead is reached. clamping thread 15. In a similar embodiment, the minimum diameter can be reduced, but the clamping does not have an entry point. In alternative embodiments, with or without an entry point, the minimum diameter may increase as lead thread 17 is wound from the termination point of helix 19 toward a mixing point 18 and may increase further beyond the mixing point 18. In alternative embodiments, the smallest or largest minimum diameter stair rungs from lead thread 17 to the next thread, but may remain constant throughout the winding of lead thread 17.

Figures 16A-16B illustrate cross-sectional side views of different lead threads 17 and anti-cross threads 16 on different male clamping members of the present invention, in which the different fasteners have different minimum diameters around the lead threads 17 These settings illustrate that it is possible to change the diameter at the roots of the lead thread without changing the anti-false threading functionality of the lead thread. In Figure 16A, the clamp 10 has a cylindrical entry point 43 that has a diameter greater than the minimum diameter of the anti-cross thread 16 and only extends as far as the lead thread 17, such that the flank 17b of the lead thread exists on the right side of lead thread 17 but there is no flank on the other side. In Figure 16B, the clamp 10 has a cylindrical entry point 43 that has a diameter greater than the minimum diameter of the anti-cross thread 16 and extends to the anti-cross thread 17, such that there is no thread. lead 17 protruding through entry point 43. This illustrates how a lead thread 17 can be shortened from one and a fifth windings to approximately one wrap where a portion of the lead thread is covered by an entry point 43 of relatively larger diameter. In Figure 16C, the clamp 10 has a cylindrical entry point 44 that has a diameter smaller than the minimum diameter of the anti-cross thread 16 and the entry point 44 and only extends to the leading thread 17, of such that the flank of the lead thread 17e is larger than the flank of the lead thread 17b. In Figure 16D, the clamp 10 has a cylindrical entry point 44 that has a diameter less than the minimum diameter of the anti-cross thread 16 and the entry point 44 and extends to the anti-cross thread 16, of such that the flanks 17e and 17f of the lead thread are of the same or almost the same size.

The present invention, therefore, is well adapted to realize the objects and achieve the aforementioned ends and advantages, as well as others inherent therein. While a presently preferred embodiment of the invention has been provided for the purpose of disclosure, numerous changes to the details or procedures to achieve the desired results will readily occur to those skilled in the art.

Claims (11)

1. An anti-false threaded fastening system comprising: a female fastening member (30) comprising: at least one female locking thread formed on an interior of the female locking member; at least one female lead thread (31) formed within the female clamp member (30); a male fixation member (10) comprising: a shaft (12) having a leading end (14) for insertion within the female fixation member (30); at least one male locking thread (11) formed on the outside of the shaft (12) as a plurality of thread windings adapted to mate with the female locking thread; characterized because at least one male lead thread (17) formed on the outside of the shaft (12) at the leading end (14) which is at least half a wrap around the shaft (12) and comprises a curved profile defined by an arc having a radius approximately equal to a radius of an arc that is tangent to both flanks of a thread profile (25) of the at least one male fastening thread (11) and below the pitch line of the at least one thread male fixing (11). 2. An anti-false threaded fastening system comprising: a female fastening member (30) comprising: at least one female locking thread formed inside the female locking member; at least one female lead thread (31) formed within the female clamp member (30); a male fixation member (10) comprising: a shaft (12) having a leading end (14) for insertion within the female fixation member (30); at least one male locking thread (11) formed on the outside of the shaft (12) as a plurality of thread windings adapted to mate with the female locking thread; characterized because at least one male lead thread (17) formed on the outside of the shaft (12) at the leading end (14) that is at least half a wrap around the shaft (12) and is shorter at a leading end (19) of the male lead thread winding (17) and higher at the other end (18) of the male lead thread winding (17), wherein the at least one male lead thread (17) comprises a vertex having a height that changes at a substantially constant rate between the ends (18, 19) of the male lead thread (17) winding, and wherein the male lead (17) comprises a male lead thread flank that is anchored to the root of an adjacent thread winding along the entire length of the male lead thread (17). An anti-false thread fastening system according to one of the preceding claims, wherein the male lead thread (17) is at least a three-quarter wrap around the shaft (12). An anti-false threaded fastening system according to one of the preceding claims 1-2, in which the male lead thread (17) is at least one and one-fifth windings around the shaft (12) . An anti-false thread fastening system according to one of the preceding claims 1-2, wherein the male thread profiles in each cross section between the ends of the male lead thread are defined by arches having approximately the same radius. An anti-false thread fastening system according to claim 1, wherein at least one male lead thread (17) is shorter at a leading end (19) of the male lead thread (17) ) and higher at the other end (18) of the male lead thread (17) winding, wherein the male lead thread (17) comprises a vertex having a height that changes at a substantially constant rate between the ends (18, 19) of the male lead thread winding (17). An anti-false thread fastening system according to claim 1, wherein the male lead thread (17) comprises a male lead thread flank which is anchored to the root of a thread winding adjacent to along the entire length of the male lead thread. An anti-false thread fastening system according to one of the preceding claims 1-2, in which a helix with continuous thread comprises the at least one male lead thread (17) and the at least one male thread male fixing (11). An anti-false threaded fastening system according to one of the preceding claims 1-2, further comprising at least one male anti-cross thread (16) extending over the female fastening threads of the fastening member female (30) when the male and female fixation members (10, 30) rotate relative to each other, whereby a longitudinal axis of the shaft (12) and a longitudinal axis of the female fixation member (30) are substantially collinearly aligned . 10. An anti-false threaded fastening system according to one of the preceding claims 1-2, further comprising at least one male anti-cross thread (16) that aligns a longitudinal axis of the axis (12) and an axis longitudinal thread of the female fixing member (30), wherein a helix with continuous thread comprises at least one male lead thread (17), the at least one male anti-cross thread (16), and the at least one male thread male fixing (11). An anti-false threaded fastening system according to one of the preceding claims 1-2, further comprising an entry point (19) formed at the leading end (14) of the shaft (12).